JPH0367861A - Adjusting mechanism for chopper fold timing - Google Patents

Abstract

PURPOSE:To adjust chopper fold timing without stopping a machine by adjusting the timing between the conveyance of a fold leaf by a conveyor belt and the vertical movement of a chopper blade. CONSTITUTION:For adjusting chopper fold timing, a motor 18 is driven to rotate an eccentric shaft 5 through bevel gears 14, 15. Following this rotation, an eccentric gear 7, supported to an eccentric part 5E of the eccentric shaft 5, is rolled along internal teeth of the first and second internal gears 6 and 8. Here, because the second internal gear 8 is provided with one tooth less than the first internal gear 6, a slight differential movement is generated in the direction of rotation between the first and second internal gears 6 and 8 due to rolling of the eccentric gear 7. The rotation of the second internal gear 8, with a phase changed as compared with the rotation of the first internal gear 6, that is, a shaft 1, is transmitted to a gear 9B, gear 10, chopper blade drive shaft 11, flange 11A and an eccentric pin 13, and the oscillation timing of a chopper arm 12B, with a bearing 12C serving as a supporting point, is adjusted.

Description

DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to a mechanism for adjusting chopper folding timing of a folding machine attached to a printing machine.

[Background technology]

Conventionally, in rotary printing presses, etc., the drive system of the folding machine is used to synchronously drive the chopper arm and the conveyor belt, so that the timing of the conveyance of signatures by the conveyor belt and the swinging of the chopper arm is synchronized. Folding is being done.

At this time, if the conveyance belt speed changes with a change in printing press speed, the timing of chopper folding of the signatures may be shifted due to slippage of the signatures on the belt, influence of inertia of the signatures, and the like.

If the timing of chopper folding is off, there is a problem that the signatures may be torn or damaged, resulting in product defects.

Therefore, if the timing of chopper folding is off, it is necessary to adjust the timing of swinging of the chopper arm and conveyance of signatures.

Conventionally, this timing adjustment has been performed by adjusting the meshing of helical gears provided in the drive system of the chopper arm. In other words, by moving one fixed helical gear in the axial direction and changing their meshing, the phase angle of the rotation of the chopper arm drive system can be changed and the swing timing can be changed. was adjusting.

[Problem to be solved by the invention]

However, although the adjustment range of the phase angle due to the meshing of helical gears is proportional to the lead angle, the movement range of the other helical gear is limited to the range where it meshes with one helical gear. If the deviation in the folding timing exceeds a certain limit, the timing cannot be adjusted.

Therefore, there was a problem in that the machine had to be stopped once to adjust the timing.

An object of the present invention is to enable continuous, stepless and unlimited adjustment of the timing between the conveyance of signatures by the conveyor belt and the swinging of the chopper arm, and to adjust the timing of chopper folding without stopping the machine during operation. The objective is to provide an adjustment mechanism that can perform the following.

[Means to solve the problem]

The chopper folding timing adjustment mechanism according to the present invention includes a chopper arm and a conveyor belt that are synchronously driven using a drive system of a folding machine attached to a printing press, and a drive system for at least one of the chopper arm and the conveyor belt. A differential mechanism is provided therein to adjust the timing of chopper folding, and the timing of the conveyance of signatures by the conveyor belt and the swinging of the chopper arm is adjusted.

Further, the differential mechanism has a gear fixed to a shaft connected to a drive system of the folding machine, external teeth that mesh with the gear, and is rotatable to a non-eccentric part of the eccentric shaft having an eccentric part. an eccentric gear that meshes with the internal teeth of the first internal gear and is rotatably supported on the eccentric portion of the eccentric shaft; and an internal tooth that meshes with the eccentric gear. and a second internal gear having external teeth that mesh with the gear train on the chopper arm side and rotatably supported on the non-eccentric part of the eccentric shaft, Each internal tooth of the second internal gear is configured to have the same pitch circle and a different number of teeth, and the chopper arm swings via a gear train meshing with the external teeth of the second internal gear. You can use one configured as follows.

Further, the eccentric shaft of the differential mechanism can be driven by a servo motor controlled by a computer, or driven by rotation of a crank handle that can be detachably attached to the end of the eccentric shaft.

[Effect]

The chopper folding timing adjustment mechanism of the present invention operates as follows.

If the differential mechanism provided in the drive system of at least one of the chopper arm and the conveyor belt is not activated, the chopper folding timing will be changed because the chopper arm and conveyor belt folding machine are synchronously driven using the drive systems of the chopper arm and the conveyor belt folding machine.゛ is maintained constant.

On the other hand, when the differential mechanism is operated, the output of the differential mechanism is continuously adjusted in a stepless and unlimited manner, so that the chopper folding timing is also continuously adjusted in a stepless and unlimited manner. Therefore, even if the timing between the swinging of the chopper arm and the conveyance of signatures by the conveyor belt is misaligned due to changes in conveyor belt speed, etc., the chopper folding timing can be changed without stopping the machine by operating the differential mechanism. Adjustments will be made.

〔Example〕

Hereinafter, one embodiment of the present invention will be described based on the drawings.

FIG. 1 shows the configuration of the drive system of this embodiment.

A folding machine including a chopper folding device 91 is connected to a motor 9 of a printing press.
It is driven by a drive system 92 connected to 3. This drive system 92 includes a drive system 94 for the chopper arm 12 and a drive system 94 for the signature 3.
A drive system 95 for the conveyor belt 21 that conveys the zero is connected thereto.

A differential mechanism 96 is included in the drive system 94 of the chopper arm 12.
A chopper crankshaft 11 that swings the chopper arm 12 is also provided. Note that this differential mechanism 96 is
As shown in FIG. 1, it may be provided in the drive system 95 of the conveyor belt 21, or it may be provided in each drive system 94, 95, respectively.

FIG. 2 shows the configuration of the drive system 94 and differential mechanism 96 of the chopper arm 12, and FIG. 3 shows the Z arrow view in FIG.

In FIG. 2, the shaft 1 of the drive system 92 of the folding machine is connected to a shaft 3 via a 1-luck limiter 2, and a spur gear 4 is fixed to the end of the shaft 3.

The spur gear 4 meshes with the external teeth of a first internal gear 6, and the first internal gear 6 is rotated via a bearing 5A on a non-eccentric portion of an eccentric shaft 5 rotatably supported by a frame (not shown). Supported for free movement.

An eccentric gear 7 rotatably supported by an eccentric portion 5E of the eccentric shaft 5 via a bearing 5B is meshed with the internal teeth of the first internal gear 6. The eccentric gear 7 meshes with the internal teeth of a second internal gear 8 that is rotatably supported by the non-eccentric portion of the eccentric shaft 5 via a bearing 5C. The internal teeth of the second internal gear 8 have the same pitch circle as the internal teeth of the first internal gear 6, and are a so-called shifted gear having one less tooth.

A spur gear 9B supported by a shaft 9 via a bearing 9A is engaged with the external teeth of the second internal gear 8, and a spur gear 10 fixed to one end of a chopper crankshaft 11 is engaged with the spur gear 9B. are engaged.

A substantially disk-shaped flange IIA is fixed to the other end of the chopper crankshaft 11, and an eccentric pin 1 is attached to this flange IIA.
3 is fixed.

As shown in FIG. 3, the eccentric pin 13 is supported by a bearing 12A fixed to one end of the chopper arm 12. Further, the chopper arm 12 is provided with a chopper blade 12B at one end thereof, and the other end is provided with a transport platform 2.
It is rotatably supported by a bearing 12, C fixed at 0.

A conveyor belt 21 that is rotationally driven by a drive system 95 is disposed on the conveyor table 20 , and the signature 30 is conveyed by the conveyor belt 21 .

On the other hand, a bevel gear 14 is fixed to one end of the eccentric shaft 5. A bevel gear 15 fixed to an output shaft 16 of a motor 18 is meshed with the bevel gear 14, and a potentiometer 17 is further connected to the output shaft 16 via a coupling 17A.

Here, a spur gear 4, an eccentric shaft 5, a first . A differential mechanism 96 is constituted by a differential gear mechanism including second internal gears 6 and 8 and eccentric gear 7.

Next, the operation of this embodiment will be explained.

When the folding machine is driven, the rotation from the drive system 92 of the folding machine is caused by shaft 1.
is transmitted to the shaft 3 of the drive system 94 via the torque limiter 2.
is transmitted to rotate the spur gear 4.

The rotation of the spur gear 4 is transmitted in the order of the first internal gear 6, the eccentric gear 7, the second internal gear 8, the spur gear 9B, and the spur gear 10 without rotating the eccentric shaft 5, and finally to the chopper crankshaft. 1
Rotate 1.

As the chopper crankshaft 11 rotates, the flange IIA
The chopper arm 12, which is connected by an eccentric pin 13 provided therein, swings about a bearing 12c as a fulcrum.

On the other hand, the conveyor belt 2 is driven by a drive system 95 branched from the shaft 1.
1 is rotationally driven, and the signatures 30 are sequentially conveyed by the drive. This signature 30 is produced by the swinging chopper arm 12.
are folded by the blades 12B, so that chopper folding is performed continuously.

Here, when the conveyance speed of the signature 30 is changed, the signature 30
The timing between the conveyance of the signature 30 and the swinging of the chopper arm 12 may deviate due to slipping on the belt 21 or the influence of the inertia of the signature 30.

To adjust the timing of this chopper folding, the motor 18 is driven to rotate the eccentric shaft 5 via the bevel gears 14 and 15. With this rotation, the eccentric gear 7 supported by the eccentric portion 5E of the eccentric shaft 5 is rotated between the internal teeth of the first internal gear 6 and the second internal gear.
Transfer along the internal teeth of the internal gear 8. At this time, since the second internal gear 8 has one less tooth than the first internal gear 6, the rotation direction of the first internal gear 6 and the second internal gear 8 is different due to the transfer of the eccentric gear 7. A slight difference occurs between the two.

The rotation of the second internal gear 8, whose phase has been changed compared to the rotation of the first internal gear 6, that is, the shaft l, is transmitted to the spur gear 9B, the spur gear IO, the chopper crankshaft 11, the flange 1lA1, and the eccentric pin 13. , the swing timing of the chopper arm 12 using the bearing 12C as a fulcrum is adjusted.

On the other hand, a drive system 95 branched from the shaft 1 rotates the belt 21 to convey the signature 30. Therefore, the transport bell) 2
1 drive system 95, the chopper arm 12 drive system 9
The phase of rotation of No. 4 is continuously adjusted steplessly and without limit, and the timing of chopper folding is freely changed.

According to this embodiment with such a configuration, the following effects are achieved.

That is, the spur gear 4 is connected to the drive system 94 of the chopper arm 12.
, eccentric shaft 5, first . Since the differential mechanism 96 consisting of the second internal gears 6 and 8 and the eccentric gear 7 is provided, the rotational phase of the drive system 94 of the chopper arm 12 with respect to the drive system 95 of the conveyor belt 21 that conveys the signatures 30 is can be adjusted continuously, steplessly and without limit. Therefore, the timing of chopper folding can be adjusted freely without stopping the machine.

Further, this timing adjustment is performed by moving the eccentric shaft 5 that supports each gear 6, 7° 8 to the motor 18 and the potentiometer 1.
7, the timing adjustment work can be performed easily and accurately.

Further, the differential mechanism 96 is connected to the spur gear 4, the eccentric shaft 5, the first . Since it is composed of the second internal gears 6, 8 and the eccentric gear 7 that meshes with the internal teeth of each gear 6, 8, the overall size can be reduced.

Therefore, the installation space within the folding machine can be reduced, and the present invention can be easily applied to existing folding machines.

Further, unlike in the past, it is not necessary to use a helical gear, and the normally used spur gear 4 and internal gear 6.8 can be used, so manufacturing costs can be reduced.

Note that the present invention is not limited to the configurations of the above-mentioned embodiments, and the present invention includes modifications within a range that can achieve the object of the present invention.

For example, in the embodiment described above, the differential mechanism 96 includes the spur gear 4, the eccentric shaft 5, the first... Although the differential gear mechanism includes the second internal gears 6 and 8 and the eccentric gear 7, a differential gear mechanism having another configuration may be used.

That is, as shown in FIGS. 4 and 5, the drive system 9
A spur gear 72 fixed to the drive shaft 71 on the second side, a spur gear 74 fixed to the drive shaft 73 of the 12 chopper arms,
A differential mechanism may be constructed by the differential gear mechanism 70 having only external gears and spur gears 75 meshing with the double-handed gears 72 and 74, without using internal gears. The spur gears 72 and 74 are configured to have the same pitch diameter and different numbers of teeth due to dislocation, and the spur gear 75 is rotatably supported by an eccentric shaft 77 of an arm 76 rotated by the motor 18. There is.

Also in such a differential gear mechanism 70, the arm 76 is rotated by the motor 18, and the spur gear 75 is connected to the spur gear 72.
By rolling along the drive shaft 74, the drive shaft 71 and the drive shaft 7
3, a differential occurs in the rotation direction and the timing of chopper folding is adjusted.

Further, as shown in FIG. 6, the spur gears 72 and 74 are configured to have different pitch diameters and numbers of teeth, and the spur gear 75 is configured to be a stepped gear that meshes with each of the spur gears 72 and 74. However, the same operation and effect as the differential gear mechanism 70 shown in FIG. 4 can be obtained.

Furthermore, the differential mechanism is not limited to one using gears, and as shown in FIGS. 7 and 8, a drive shaft 71. ．． 7
Timing pulleys 8], 82 fixed to 3 respectively.
, timing pulleys 83 and 84 rotatably supported by the eccentric shaft 77 of the arm 76, and timing pulleys 81 .
A differential mechanism 80 having timing belts 85 and 86 extending between 83 degrees and 82 degrees and 84 degrees, respectively, may be used. Even in such a differential mechanism 80, the chopper folding timing can be adjusted by rotating the arm 7G with the motor 18 via the timing belt 87.

Furthermore, as the differential mechanism, a so-called planetary gear mechanism 100, which includes a sun gear 101, a planetary gear 1.degree. 2, and an internal gear 103, may be used, as shown in FIGS. 9 and 10.

Furthermore, as shown in FIG. 11, the case Ill is rotated by the motor 18, the bevel gears 112, 11.3 fixed to the drive shafts 71, 73, and the rotating shaft 114 in the cases 1, 11 are rotated. A differential gear mechanism 110 having a configuration similar to a so-called automobile differential gear, which is provided with bevel gears 115 and 116 that are freely supported and mesh with bevel gears 112 and 113, may be used.

In short, various types of differential mechanisms can be used in the present invention, and these may be selected and used as appropriate in implementation.

In addition, when a differential gear mechanism is used as the differential mechanism,
Helical gears may be used instead of spur gears.

Further, the drive source for rotating and driving the eccentric shaft 5 is not limited to the motor 18 and the potentiometer 17, but may also be a commercially available pulse motor or an AC or DC servo motor that is publicly known and in use. At this time, if the servo motor is numerically controlled via the microcomputer 5 computer, data set in advance according to the paper quality and thickness of the signature 30 can be input into the computer, and the servo motor can be controlled based on that data. By doing so, the chopper folding timing can be set and maintained according to the type of signature 30.

In addition, without using a motor or the like, the chopper folding timing can be adjusted manually by attaching a crank handle to the end of the eccentric shaft 5 and rotating the handle while looking at the scale plate that displays the rotation angle of the eccentric shaft 5. It may also be done through In short, in the present invention, the eccentric shaft 5 can be driven either manually or automatically, and these can be freely selected according to the operator's wishes.

Furthermore, in the embodiment described above, the timing of chopper folding was adjusted by providing a differential mechanism 96 in the drive system 94 of the chopper arm 12 to adjust the timing of swinging of the chopper arm 12. As shown by the two-dot chain line,
The timing of chopper folding may be adjusted by providing a differential mechanism 96 in the drive system 95 of the conveyor belt 21 to adjust the timing of conveyance of the signatures 30 by the conveyor belt 216.

Alternatively, a differential mechanism 96 may be provided in each of the drive systems 94 and 95, and the swinging of the chopper arm 12 and the conveyance of the signatures 30 by the conveyor belt 21 may be adjusted to adjust the timing of chopper folding.

〔Effect of the invention〕

As described above, according to the chopper folding timing adjustment mechanism of the present invention, the chopper folding timing can be continuously performed steplessly and without limit, and therefore the chopper folding timing can be adjusted without stopping the machine. It has the effect of being able to

Furthermore, if a differential gear mechanism is used as the differential mechanism, the differential mechanism can be made smaller and the installation space can be reduced.

Furthermore, if the eccentric shaft of the differential gear mechanism is driven using a servo motor controlled by a computer, there is an effect that the chopper folding timing can be adjusted depending on the type of signature.

Furthermore, by attaching a crank handle to the eccentric shaft, it is possible to manually adjust the drive of the eccentric shaft, that is, the chopper folding timing.

[Brief explanation of drawings]

Figures 1 to 3 are diagrams showing one embodiment of the present invention, with Figure 1 being a schematic diagram showing the configuration of the drive system of the folding machine, and Figure 2 showing the drive system and differential mechanism of the chopper arm. Floor plan, 3rd
The figure is a sectional view showing the Z arrow direction in Fig. 2, Fig. 4 is a sectional view showing a modified example of the differential mechanism, Fig. 5 is a sectional view taken along the line ■-■ in Fig. 4, and Fig. 6 is a sectional view showing a modification of the differential mechanism. The figure is a sectional view showing another modified example of the differential mechanism, FIG. 7 is a sectional view showing another modified example of the differential mechanism, FIG. 8 is a sectional view taken along the line ■-■ in FIG. 7, FIG. 9 is a sectional view showing another modification of the differential mechanism, and FIG. 10 is a cross-sectional view taken along the line X-X in FIG.
FIG. 11 is a sectional view taken along the line and shows another modification of the differential mechanism. DESCRIPTION OF SYMBOLS 1... Shaft, 4.9B, 10... Spur gear, 5... Eccentric shaft, 6... First internal gear, 7... Eccentric gear, 8...
...Second internal gear, 11...Chopper crankshaft, 1
2...Chiyo Soba arm, 12B...Chopper blade, 18...Motor, 21...Transport belt, 30
... signature, 70,110 ... differential gear mechanism, 80.
96...Differential mechanism, 91...Chopper folding device, 9
2,94.95... Drive system, 100... Planetary gear mechanism.

Claims (4)

[Claims] (1) A chopper arm and a conveyor belt are provided that are driven synchronously using the drive system of a folding machine attached to the printing press, and the timing of chopper folding is adjusted in the drive system of at least one of the chopper arm and the conveyor belt. What is claimed is: 1. A chopper folding timing adjustment mechanism, comprising: a differential mechanism for adjusting the timing between the conveyance of signatures by the conveyance belt and the swinging of the chopper arm; (2) The chopper folding timing adjustment mechanism according to claim 1, wherein the differential mechanism has a gear fixed to a shaft connected to a drive system of the folding machine, and external teeth meshing with the gear. A first rotatably supported by a non-eccentric part of an eccentric shaft having an eccentric part.
an internal gear, an eccentric gear that meshes with the internal teeth of the first internal gear and is rotatably supported by the eccentric portion of the eccentric shaft, internal teeth that mesh with the eccentric gear, and a gear on the chopper arm side. a second internal gear having external teeth meshing with the row and rotatably supported on the non-eccentric portion of the eccentric shaft, each internal tooth of the first and second internal gears; is characterized in that the pitch circles are the same and the numbers of teeth are different, and the chopper arm is configured to swing via a gear train meshing with the external teeth of the second internal gear. Adjustment mechanism for chopper folding timing. (3) The chopper folding timing adjustment mechanism according to claim 2, wherein the eccentric shaft of the differential mechanism is driven by a servo motor controlled by a computer. (4) The chopper folding timing adjustment mechanism according to claim 2, wherein the eccentric shaft of the differential mechanism is driven by rotation of a crank handle that is detachably attached to an end of the eccentric shaft. mechanism.